Note : Les descriptions sont présentées dans la langue officielle dans laquelle elles ont été soumises.
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BACKGROUND OF T~IE INVENTION
It long has been recognized that the conventional universal joint
~ball and socket) interconnection between the trailer hitch of a towing
vehicle such as an automobile or light truck and the trailer tongue of a towed
vehicle, of which camper and boat trailers are but two examples, permits the
possibility of undesirable sway of the towed vehicle. Operation of such
tandem vehicle combinations on rough, uneven or winding roads, as well as
under cross-wind conditions, as well as inherent suspension characteristics,
gives rise to such sway.
In order to minimize or eliminate this tendency of the towed vehicle
to sway, the prior art has detailed a variety of sway control devices that
provide friction forces that oppose lateral movement of the towed vehicle
relative to the towing vehicle. These friction forces are overcome during
operator controlled vehicle maneuvering as during turning and such lateral
movement permitted. Examples of such prior art devices are dlsclosed by
United States patents 3,552,771, issued January 5, 1971, 3,542,395, issued
November 24, 1970 and 3,294,421, issued Decem'ber 27, 1966.
An object of this invention is to provide an improved friction sway
control device for towed vehicles that functions in a manner superior to those
previously available. A further object of this invention is to provide a
friction sway control device of improved performance, but ~hich has a simple,
uncomplicated design that promotes ease and economy of manufacture and
assembly to the vehicles associated therewith, as well as relia~ility of oper-
ation.
This invention relates to apparatus for controlling sway between a
towed vehicle having a trailer tongue member and a towing vehicle having a
trailer hitch member to which said tongue member is secured, a bar having at
least one planar bar surface, first mounting means securing said bar to one of
said members while permitting universal pivotal movement of said bar relative
to said one member about said first mounting means3 friction brake means, and
second mounting means securing said brake means to the other of said members
while permitting pivotal movement therebetween about only a single axis, said
brake means engaging said bar and having at least one friction surface fric-
.
tionally contacting said planar bar surface, said friction surface being
planar and parallel to both said axis and said planar bar surface, said brake
mcans and said second mounting means being spaced from said bar a distance
sufficient to permit substantial swinging movement of said bar about said
first mounting means and parallel to said axis, the dimension of said fri.ction
surface measured along a line parallel to said axis being substantially great-
~:~ er than the corresponding dimension of said planar bar surface such that upon
said substantial swinging movement of said bar about said first mounting means
in directions parallel to said axis said friction surface and said planar bar
10 surface remain in friction contact.
More particularly, this invention relates to apparatus for control-
ling sway between a towed vehicle having a trailer tongue member and a towing
vehicle having a trailer hitch member to which said tongue member is secured,
an elongate bar having a pair of flat parallel sides, universal pivot means
securing said bar to one of said members and permitting universal pivotal
movement of said bar relative to said one member about said pivot means, fric-
tion brake means, mounting means securing sa:id brake means to the other of
said members while permitting pi.votal movement therebetween about only a
single axis parallel to said sides, said brake means including outer housing
O means having an open passage extending therethrough and planar friction shoe
surfaces within said housing and partially defining said passage, said bar
extending through said passage and being capable of reciprocal movement there-
in normal to said axis and substantial swinging movement therein parallel to
said axis and about said pivot means, at least one of said shoe surfaces
frictionally engaging at least one of said sides, the dimension of said shoe
surfaces measured along a line parallel to said axis being substantially
greater than the width of said sides measured along a line parallel to said
axis for allowing continuous frictional engagement between at least one of
said shoe surfaces and one of said sides during said substantial swinging
movement of said bar.
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DESCRIPTION OF THE DRAWINGS
Figure 1 is a schematic top view representing a towing and towed
vehicle tandem with the trailer sway control device of this invention associ-
ated therewith;
Figure 2 is an isometric view of the trailer sway control device of
Figure 1, and including portions of the towing vehicle trailer hitch and
towed vehicle trailer tongue;
Figure 3 is a top view with parts broken away and hidden lines
shown in phantom, of the trailer sway device of Figure 2;
Figure 4 is a side elevation view, with parts broken away and hid-
den lines represented in phantom, of the device of Figure 2;
Figure 5 is a section view taken along the line 5-5 of Figure 4;
Figure 6 is a section view taken along the line 6-6 of Figure 4; and
Figure 7 is a section view taken along the line 7-7 of Figure 4.
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DETAILED DESCRIPTION OF THE INVENTION
Referring now in detail to the drawings, and in particular
to Figure 1 thereof, the numeral 8 denotes generally a towing
vehicle secured to and towing a towed vehicle 10. The inter-
connection between the towing vehicle 8 and towed vehicle 10
is by means of a trailer hitch 12 secured to the towing vehicle
and a trailer tongue 14 secured to the towed vehicle. While
the trailer sway control device of this invention may be
utilized with trailer tongue constructions of various types,
a so-called "A-fxame" trailer tongue is shown in Figure 1 for
illustrative purposes and includes a pair of relatively
angularly positioned structural members 14a and 14b that
converge proximate the trailer hitch 12. Secured to trailer
tongue 14 at the convergence of members 14a and 14b is a coup-
ler 16 as is well known in the art. Coupler 16 comprises a
female member having an arcuate internal configuration that
receives a male member or ball that is part of trailer hitch
12. Such a hitching relationship is well known in the art to
provide a universal pivotal coupling ~etween the towing and
towed vehicle.
The trailer sway control device of this invention is
designated generally by the reference numeral 18. It is shown
in a position lying generally parallel to trailer-tongue
element 14a, although as readily may be appreciated by one
having skill in the art, the device 18 may be positioned along
either trailer tongue element, or along a single element trailer
tongue.
Device 18 includes a friction bar 20 having a rectangular
cross section with a female socket member 22 secured as by
welding to one end thereof. Socket member 22 is open-ended
with a partial spherical internal configuration in order to
receive a partially spherical ball member 24. Member 24
includes a threaded shank portion 24a that extends through
an aperture in an adapter bar 28 and is secured to the adapter
bar by nut 26. Adapter bar 28, at its end remote from member
24, is fixably secured to the trailer hitch 12 as by welding
or other suitable means.
To facilitate a removable interconnection between socket
member 22 and ball member 24, a slot 30 is formed through
socket member 22 at a position between the open end of the
socket member and the center of the spherical portion of
the ball when the ball member 24 fully is received in socket
member 22. A retaining spring clip 32 has one end 32a thereof
which extends through an aperture in bar 2~ and is secured in
this position by a jam nut 34 or any other suitable fastening
means. The end of spring clip 32 remote from end 32a extends
within the socket member 22 and has a U-shaped projection proxi-
mate the end portion thereof.
When this portion of spring clip 32 is aligned within
socket member 22 with slot 30, the resilient force of the spring
material from which the spring clip is formed causes projection
32b to extend into and be held in slot 30, thereby locking
socket member 22 onto ball member 2~. When it is desired to
separate ball member 2~ and socket member 22, spring clip end
32b, which is accessible from the exterior of the socket
member via slot 30, need only be depressed manually out of
slot 30 while socket member 22 is lifted from ball member 24.
It thus may be seen that by means of the ball and socket
connection provided by socket member 22 and ball member 24,
as well as the rigid interconnection of the ball member to
the trailer hitch 12 by adapter bar 28, friction bar 20
effectively may be universally pivotally connected to the
trailer hitch 12 of vehicle 8.
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~ s best may be seen in Figures 2, 3 and 4, the trailer
sway control device 18 includes a brake assembly designated
generally by the reference numeral 36. The mounting of brake
assembly 36 is accomplished by means of a bracket 38 secured
to trailer tongue Inember 14a by fasteners 40. Bracket 38
includes a pair of spaced apart arms 38a and 38b that extend
angularly from trailer tongue 14a. Each of bracket arms 38a
and 38b has formed therethrough holes 38c and 38d, respectively,
which holes 38c and 38d are aligned. Internally threaded
bushings 42 and 43 are positioned in holes 38c and 38d,
respectively. Pivot nuts 44 and 46 are threaded through and
extend beyond bushings 42 and 43 respectively.
The purpose of pivot nuts 44 and 46 is to provide single
axis pivot means to which brake assembly 36 is attached. Brake
assembly 36 includes an outer housing 48 in the form of a
rectangular tube having aligned apertures 48a and 48b extending
therethrough in the opposed short dimension sides thereof.
Pivot nut shanks ~4a and 46a, which are no-t threaded at their
extremities, extend into and through apertures 48a and 48b,
respectively, of brake assembly housing 48. It thus may be
seen that by means of bracket 38 and the pivot assembly
described herebefore, brak0 assembly 36 operatively is pivotally
connected to the towed vehicle trailer tongue 14 in a manner
permitting pivotal movement by the brake assembly about only
a single axis, which axis extends through the centers of pivot
nuts 44 and 46.
With reference to Figures 5 and 6 of the drawings and the
details of brake assembly 36, it may be seen that positioned
within the brake assembly housing 48 are a pair of brake shoes
50 and 52, having opposed surfaces 54 and 56, respectively,
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of friction material formed thereon. The friction material
surfaces are planar, lie parallel to the pivot axis of the
brake assembly and contact opposite long dimension sides of
friction bar 20 that extends through the brake assembly. As
best seen in Figures 4 and 6, brake shoe 50 has an upper slot
58 and a lower slot 60 formed therein at its opposite vertical
extremities. Brake shoe 52 has identical slots formed therein
(unnumbered) each of which are aligned with one of slots 58
and 60. A bolt 62, threaded along a portion of its shank,
extends through the upper slots of brake shoes 50 and 52 as
well as through aligned apertures (unnumbered) in the long
dimension sides of housing 48. A similar bolt 64 extends
through the lower brake shoe slots and housing 48. The head
end of bolt 64 is formed with a handle projection 64a that
extends to the exterior of brake assembly 36. The function
and purpose of handle projection 64a will be explained in
detail below.
A resilient spring member 66 is positioned hetween housing
48 and trailer tongue element 14a and includes a C-shaped
portion that extends through an opening 74 in a long dimension
side of housing 48 so that the C-shaped spring portion bears
upon the side of brake shoe 52 remote from friction material
56. Bolts 62 and 64 extend through openings 66a and 66b,
respectively, formed in spring 66 and are engaged by nuts 68
and 70, respectively. A spring clip 72, formed from a sheet
of rigid material, surrounds nuts 68 and 70 and has end portions
72a and 72b engaging opposite ends of spring 66 so that spring
clip 72 is locked against movement relative to the spring 66,
and therefore locks nuts 68 and 70 against rotation relative
to bolts 62 and 64 respectively.
As may be seen from the above description of thedetails
of construction of brake assembly 36, it readily may be
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apprecia-ted that bolt 62 and nut 68 may be engaged to pre-
determined relative positions to bring friction material
surfaces 54 and 56 into engagement with friction bar 20.
Thereafter, by manual manipulation of handle projection 64a
of bolt 64, the frictional forces between bar 20 and friction
surfaces 54 and 56 may be increased or decreased by tightening
or loosening nut 70 upon bolt 64. As will be explained in
detail below, the magnitude of the frictional forces between
the bar 20 and the friction elements of the brake assembly 36
determines the magnitude of the deterrent to sway provided by
the trailer sway control device of this invention.
The function of the trailer sway control device described
in detail above is as follows. As is well known, the conven-
tional universal pivotal attachment between towed and towing
vehicles such as is illustrated in Figure 1, allows relative
transverse motion between the two vehicles. Such motion is
necessary, of course, during maneuvering of the tandem vehicle
arrangement, such as turning. However, sway or transverse
movement of the towed vehicle 10 relative to the towing
vehicle 8 durin~ straight line high~ay operation is undesirable.
It readily may be appreciated that when such relative trans-
verse movement occurs, there is an angular rotation of trailer
tongue 14 about a vertical axis extending through the trailer
hitch of the towing vehicle. Because friction bar 20 operatively
is secured to the towing vehicle and brake assembly 36 opera-
tively is secured to the trailer tongue 14 of the towed vehicle,
this relative angular movement will cause relative movement
of the brake assembly 36 along the length of the friction bar
20. The friction forces generated between the friction bar
and the friction surfaces of the brake assembly 36 thus tend
to resist the transverse or lateral movement (sway) of the
towed vehicle. The degree of resistance to such transverse
movement may be adjusted for particular road conditions and/or
vehicle characteristics by varying the friction forces
between bar 20 and friction surfaces 54 and 56. This adjust-
ment in frictional forces and hence the magnitude of sway
control is accomplished by manual manipulation of handle 64a
as described above.
All of the functions heretofore described for the sway
control device of this invention are well known in the art for
friction sway control devices of this type, for example, the
device disclosed in U. S. patent 3,294,421 described above.
Because of the transverse relative movement between towed
and towing vehicle which is desirable during maneuvering, as
well as other relative movements between the two vehicles, such
as relative vertical movements and relative twisting movements
as may be encountered on uneven, undulating roads, it is
necessary to provide for relative movement between the friction
bar 20 and brake assembly 36 in addition to the longitudinal
relative movement along the axis of the friction bar 20. Prior
art sway control devices of the friction member-brake type
either have not accommodated such relative movement to a
sufficient extent, or in the case of previously mentioned U. S.
patent 3,294,421, have accommodated such relative movement by
universal mounting of both the friction member (bar 20 in this
invention) and the brake shoe member (assembly 36 of this
invention).
In contradistinction and as part of this invention, it was
determined that only "two degree" freedom of movement was
required between the sway control device element (friction
(friction member or brake assembly) mounted to the towed
vehicle to accommodate the relative movements between the two
tandem vehicles. It was this determination that allows the
unique mounting of brake assembly 36 as illustrated herein,
wherein the brake assembly is pivotally secured to the trailer
~ongue element 14a about only a single pivot axis, the axis
that extends through the centers of pivot nuts 44 and 46. As
illustrated, this mounting of brake assembly 36 allows hori-
zontal rotation of the brake assembly about only a vertical
pivot axis. However, as readily may be appreciated, this
pivot axis could be oriented at any angular orientation to
the vertical so long as pivotal movement about a single axis
is provided. This permitted pivotal movement provides one
degree of freedom of motion necessary to accommodate relative
vehicular movement.
The second degree of freedom of movement is provided by
the unique dimensioning of the brake assembly 36 relative
to the cross sectional size of friction bar 20. As is best
illustrated in Figures 5 and 6 of the drawings, substantial
clearance is provided above and below the short dimension
sides of the rectangular cross sectionaled area friction bar
20. This allows the friction bar, which can pivot universally
about ball member 24, to move relative to brake assembly 36 in
a direction parallel to the pivot axis of the brake assembly
(up and down as illustrated).
Two degree freedom of movement thus is provided without
the need for universal pivotal mounting of both the brake
assembly and ~riction member and the respective vehicles to
which they are mounted.
Certain advantages are provided by the sway control
device mounting scheme of this invention. This scheme provides
for a more rigid and reliable coupling of the various parts to
one another. Furthermore, since the relative movement permitted
between the brake assembly and the trailer tongue assembly to
which it is mounted is pivotal movement about only a single
axis, and this axis passes substantially through the center of
the friction bar 20, any tendency for torsional or twisting
movement between the friction bar and the brake assembly is
minimized. Additionally, since the pivot axis of the brake
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assembly 36 extends through friction bar 20 and the propensity
for a torsional twisting on the friction bar is reduced by this
arrangement, it i5 possible -to construct the friction bar 20
of less massive dimensions with an attendant savings in material
and weight.
Still another advantage to the single pivot axis mounting
of brake assembly 36 is realized when towed vehicle 10 is
uncoupled from towing vehicle 3 as during temporary parking
or storage. The single pivot axis mount does not permit the
free end of friction bar 20, which has been uncoupled from
ball member 24, to deflect angularly towards or away from
the ground since brake assembly 36 can pivot only about the
single axis and the friction material surfaces in the brake
assembly hold bar 20 against movement relative to the brake
assembly. ~Ihile upon first impression this may seem to be a
minor feature, when a towed vehicle such as a boat trailer
manually is maneuvered as when it is positioned in a storage
area or garage, it is important that obstacles along the ground
or depresslons in the supporting surface not be engaged by any
structure that is part of the trailer. Since such trailers
often are difficult to maneuver manually and require full
strength, two handed movement by the person maneuvering the
trailer, a trailing friction member dragging along the ground
could present a serious impediment to such manual maneuvering.
It thus may be seen that this invention provides an
improved friction sway control device for tQwed vehicles that
functions in a manner believed superior tothosepreviously
available. Furthermore, this invention provides a friction
sway control device which has an uncomplicated design that is
simple and economical to manufacture and assemble and is
reliable in operation.
